EP2195166B1 - Dispositif d'encrage d'une presse à imprimer - Google Patents

Dispositif d'encrage d'une presse à imprimer Download PDF

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Publication number
EP2195166B1
EP2195166B1 EP08786488.0A EP08786488A EP2195166B1 EP 2195166 B1 EP2195166 B1 EP 2195166B1 EP 08786488 A EP08786488 A EP 08786488A EP 2195166 B1 EP2195166 B1 EP 2195166B1
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EP
European Patent Office
Prior art keywords
cylinder
rotation
drive motor
friction
drive
Prior art date
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Not-in-force
Application number
EP08786488.0A
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German (de)
English (en)
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EP2195166A1 (fr
Inventor
Michael Heinz Fischer
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Koenig and Bauer AG
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Koenig and Bauer AG
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Publication of EP2195166A1 publication Critical patent/EP2195166A1/fr
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Publication of EP2195166B1 publication Critical patent/EP2195166B1/fr
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B41—PRINTING; LINING MACHINES; TYPEWRITERS; STAMPS
    • B41F—PRINTING MACHINES OR PRESSES
    • B41F31/00—Inking arrangements or devices
    • B41F31/004—Driving means for ink rollers
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B41—PRINTING; LINING MACHINES; TYPEWRITERS; STAMPS
    • B41F—PRINTING MACHINES OR PRESSES
    • B41F31/00—Inking arrangements or devices
    • B41F31/15—Devices for moving vibrator-rollers
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B41—PRINTING; LINING MACHINES; TYPEWRITERS; STAMPS
    • B41P—INDEXING SCHEME RELATING TO PRINTING, LINING MACHINES, TYPEWRITERS, AND TO STAMPS
    • B41P2213/00—Arrangements for actuating or driving printing presses; Auxiliary devices or processes
    • B41P2213/10—Constitutive elements of driving devices
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B41—PRINTING; LINING MACHINES; TYPEWRITERS; STAMPS
    • B41P—INDEXING SCHEME RELATING TO PRINTING, LINING MACHINES, TYPEWRITERS, AND TO STAMPS
    • B41P2213/00—Arrangements for actuating or driving printing presses; Auxiliary devices or processes
    • B41P2213/10—Constitutive elements of driving devices
    • B41P2213/25—Couplings; Clutches

Definitions

  • the invention relates to an inking unit of a printing press according to the preamble of claim 1.
  • an inking unit of a printing machine for coloring a forme cylinder which has a compactor with at least one near the cylinder and a form cylinder remote distribution cylinder.
  • the form cylinder near the distribution cylinder is rotationally driven only by friction with adjacent rollers, ie it is designed to the rotational drive without a mechanical drive connection going beyond the friction to a drive motor.
  • an inking unit which has a compactor with at least one near the cylinder and a form cylinder remote friction cylinder, both of which are rotationally driven, created an improved color flow by near-cylinder region of the compactor almost undisturbed rolling of the juxtaposed rollers is achieved.
  • a reduced wear and a reduced power consumption and control effort is achieved.
  • an inking unit of a printing machine is known, wherein a distribution cylinder of the inking unit is selectively driven by a reversible auxiliary motor.
  • an inking unit in which a distribution cylinder is connected via a switchable coupling with a drive motor.
  • the GB 1 366 228 A discloses a freewheel in a gear transmission for driving a Ink roller.
  • the GB 2 019 317 A describes a paint roller, which is driven by a geared motor via a freewheel.
  • the invention has for its object to provide an inking unit of a printing press.
  • the invention is in any case realized by a Inking unit, which has a roller train with at least one distribution cylinder, a drive for all distribution cylinders in a washing function against a production direction of rotation, whereas in a production direction of rotation at least not all distribution cylinders have a drive, but at least one distribution cylinder in the production direction without drive, then by Friction is driven by at least one other roller.
  • the achievable with the present invention consist in particular in that, in particular during cleaning or a color change, an increased cleaning quality is achieved without having to give up the well-known inking.
  • At least one first distribution cylinder of a compactor roller has no drive connection to a drive motor in the production direction, but is rotationally driven in the production direction only via the frictional contact with cooperating rollers. He therefore exerts in the direction of production no forced via a mechanical drive connection with a drive motor rotational movement, while preferably a second z.
  • the inking unit or the roller train of the inking unit can be formed with its own side frame as a module.
  • the drive of the inking unit can also be designed as a gear module with releasably connected drive motor and already detachably connected outside the printing machine with the side frame of the inking unit be.
  • At least one distribution cylinder for maintenance purposes at standstill is preferably swung off by means of a pivotable connecting rod mechanism. This simplifies maintenance because accessibility is improved.
  • a printing machine, z. B. web-fed rotary printing press, in particular a multi-color web-fed rotary printing press, has a printing unit 01, in which a web of material 02, short web 02 on both sides simply or in particular successively multiple, z. B. here four times, or several tracks at the same time one or more times are printable.
  • the printing unit 01 has a plurality of, in the present case four, vertically stacked double printing units 03 for the two-sided printing in the rubber-against-rubber operation.
  • the double printing units 03 - shown here in the form of bridge or n-printing units - are each formed by two printing units 04, which each have a cylinder 06 formed as a transfer cylinder 06 and cylinder 06 as a forme cylinder; 07, z. B. printing cylinder 06; 07, and in each case have an inking unit 08 and in the case of wet offset printing additionally a dampening unit 09.
  • a (double) pressure point 05 is formed in Anstelllage.
  • the above components are only on the top double printing unit 03 of Fig. 1 denotes, wherein the stacked (double) printing units 03; 04, however, can be made identical, in particular in the embodiment of the features relevant to the invention.
  • the double printing units 03 can - as well as the below-described advantageous feature of the linear arrangement - as well contrary to the illustration in Fig. 1 as an upwardly opening U unit or as in Fig. 2 represented as Was double printing unit 03, that is, wherein the axes of rotation of the printing cylinder 06; 07 in pressure-on position in a common plane, be executed.
  • Shaping and transfer cylinder 07; 06 are z. B. with a bale width of at least two, z. B. four or even six juxtaposed standing printed pages in newspaper format, especially in broadsheet format formed.
  • At least the forme cylinder 07 can in one embodiment z. B. have a circumference which essentially corresponds to two consecutively arranged printed pages in a newspaper format. In another embodiment, the scope may correspond to a single such print page.
  • 4, 5 and 6 comprises three, the color to the printing plate of the forme cylinder 07 rollers 11, in particular applicator rollers 11, the color of a moist machine remotely changeable roller 12.1, in particular Reibzylinder 12.1 (eg., With a hard surface), a second, near the humidor Changable roller 12.2 in particular Grater cylinder 12.2, another ink or transfer roller 13 (eg, with a soft surface), a roller 14, in particular film roller 14 and a roller 16, in particular ductor or dip roller 16 from a color box 17 receives. Dipping and film roller 16; 14, which are characteristic of a film inking, can also be advantageous by another Farbzu Georgia- or -dosiersystem, z. B.
  • the soft surfaces of the application and / or transfer rollers 11; 13, short soft rollers 11; 13, are yielding in the radial direction, z. B. with a rubber layer, formed in what Fig. 2 is expressed by the concentric circles.
  • rollers 11; 12; 13; 14 of the inking 08 hired together, so dive depending on the contact pressure and / or travel the hard surfaces of the distribution cylinder 12.1; 12.2 in the soft surfaces of the respective cooperating soft rollers 11; 13 more or less far.
  • the circumferential ratios of successively rolling, cooperating rollers 11 change; 12; 13; 14th
  • a rotary positive drive by specifying a speed, z.
  • a drive motor or a corresponding mechanical drive connection to another driven component then rotates an adjacent, driven only by friction of the former roller ago soft roller depending on Eindschreibiefe with different speed.
  • this soft roller but additionally driven by a separate drive motor or additionally via friction in a second Nipstelle from another speed-determined roller ago, this can in the first case to a difference between motor-specified speed and friction caused by friction, and in the second case, there is a difference between the two speeds caused by friction. Slippage occurs at the nip points and / or the drive motor (s) are unnecessarily heavily loaded.
  • the dampening remote drive cylinder 12.1 is rotatory in the production direction only via friction with adjacent rollers 11; 13 driven and points to its rotary drive in the production direction ( Fig. 2 and 4 ) neither an additional mechanical drive connection for driving the printing cylinder 06; 07 or another rotationally driven roller of the inking unit still on its own drive motor.
  • the first distribution cylinder 12.1 predominantly over in this Example three driven by friction with the forme cylinder 07 applicator rollers 11 rotationally driven and has, regardless of the indentations in the intermediate Nipstellen substantially the peripheral speed of the forme cylinder 07 on.
  • the dampening near proximity cylinder 12.2 has, as in Fig. 2 indicated, a rotationally driving in the direction of production drive motor 18, which, however, in an in Fig.
  • the first, dampening remote drive cylinder 12.1 rotationally in the production direction only by friction with adjacent rollers 11; 13 driven, ie that it is designed to the rotational drive in the production direction without rotation beyond the friction, a torque transmitting mechanical drive connection to the drive motor 18, and that the first, remotely dampening distribution cylinder 12.1 in a washing or Jostsearchraum against the production direction of rotation rotatory is driven by the drive motor 18, that is, that it is formed to the rotational drive against production rotation direction with a torque transmitting mechanical drive connection to the drive motor 18.
  • the second, near-the wet offset cylinder 12.2 in both directions of rotation additionally forcibly driven by the drive motor 18 both in and against the production direction of rotation.
  • the dampening remote drive cylinder 12.1 has its own, only his in the direction of production only by friction with an adjacent roller 11; 13 generated rotational movement in a traversing movement forming traversing gear 19.
  • This can be advantageously designed as a cam gear, wherein z. B. a frame-mounted axial stop cooperates with a roller-fixed curved circumferential groove or a roller-fixed axial stop in a frame-fixed circumferential groove of a cam.
  • the traversing gear 19 of the first Reibzylinders 12.1 is mechanically coupled via a gear 21 with the traversing mechanism 19 of the second Reibzylinders 12.2 in an advantageous manner.
  • the two coupled traversing gear 19 is a common traversing drive 22 or traversing gear 22 and are for their traversing movement forcibly driven by a drive motor 18.
  • the forced drive of the traversing gear 22 is effected by the drive motor 18 rotatably driving the second distribution cylinder 12. 2 in the production direction of rotation (FIG. Fig. 2 and 12 ).
  • At least one distribution cylinder 12.1 of the compactor is in the pressure on position ( 4 and 5 ) in the production direction of rotation ( Fig. 4 ) exclusively via friction with at least one adjacent roller 11; 13 rotationally driven, and contrary to the production direction of rotation ( Fig. 5 ) driven by a motor.
  • in the production direction of rotation is exclusively via friction with at least one adjacent roller 11; 13 rotatably driven distribution cylinder 12.1 a dampening remoteness distribution cylinder 12.1.
  • both in and against the production direction of rotation in addition by the drive motor 18 rotatably driven distribution cylinder 12.2 is a dampening near the cylinder 12.2.
  • print on position ( 4 and 5 ) finds it in the Fig. 4 b) and 5 b ) indicated by double arrows traversing the distribution cylinder 12.1; 12.2 both in one direction of rotation in, and against the production direction of rotation instead, whereas in pressure-off position ( Fig. 6 ) no oscillation takes place at standstill.
  • the positive drive of the distribution cylinder 12.2 in the production direction of rotation is in Fig. 4b) indicated by a rotary arrow, as well as the positive drive of both distribution cylinders 12.1; 12.2 contrary to the direction of production in Fig. 5b) ,
  • Fig. 12 and 13 is an advantageous embodiment for the drive of the distribution cylinder 12.1; 12.2, wherein only the second distribution cylinder 12.2 is forcibly driven rotationally in the production direction of rotation, however, both distribution cylinders 12.1, 12.2 are axially forcibly driven in rotation via the common traversing drive 22, as well as counter to the production direction of rotation.
  • a corresponding axle section 28 of the first distribution cylinder 12. 1 has an in Fig. 18 enlarged illustrated transmission 35 in the form of a spur gear 35 with a freewheel 50 in the production direction of rotation or in the production direction of rotation no torque transmitting mechanical drive connection to the drive motor 18.
  • a direction of rotation independent coupling Under a freewheel 50 is understood in the present context, a direction of rotation independent coupling.
  • the direction of production is the direction of rotation during printing.
  • the drive connections between the drive pinion 26 and the spur gear 35 of the first friction cylinder 12.1 and between the drive pinion 26 and the spur gear 27 of the second friction cylinder 12.2 are preferably straight toothed and formed with a sufficiently large overlap in the teeth engagement for each position of the traversing movement.
  • the two distribution cylinders 12.1; 12.2 are in a side frame 31 in bearings 32, z. B. radial bearings 32 are mounted, which additionally allow an axial movement ( FIGS. 15 and 16 ).
  • a rotational drive connection between the drive motor 18 and the first distribution cylinder 12.1 in the production direction of rotation does not exist here.
  • the freewheel 50 of the gear 35 designed as a spur gear 35 can not torque in Production direction of rotation on the load-bearing clamping hub 51 (FIG.
  • Fig. 18 transmitted to the pin 29 of the first Reibzylinders 12.1.
  • Drive pinion 26 and arranged on the axle portion 28 spur gear 27 together represent a transmission, in particular reduction gear, for the rotary drive in and against the production direction of rotation.
  • Drive pinion 26 and arranged on the axle portion 28 spur gear 35 together constitute a transmission, in particular reduction gear for
  • the two drives constitute a closed and / or preassembled unit with its own housing 30. The unit can be coupled on the output side to the pins 29.
  • the traversing drive 22 is also by the drive motor 18, z. B. via a worm drive 33, 34, driven.
  • a shaft 24 disposed from the screw 33 and a screw 33 formed as a portion of the shaft 24 on a worm wheel 34 which rotatably with a perpendicular to the axis of rotation of the distribution cylinder 12.1; 12.2 extending shaft 36 is connected.
  • Each end face of the shaft 36, a driver 37 is arranged eccentrically to the axis of rotation, which in turn z. B.
  • a crank mechanism for example via a rotatably mounted on the driver 37 connecting rod 38 and a hinge 39, in the axial direction of the distribution cylinder 12.1; 12.2 pressure and zugsteif with the pins 29 of the distribution cylinder 12.1; 12.2 is connected.
  • the friction gear 19 of the dampening remote drive cylinder 12.1 and the dampening cylinder near the friction cylinder 12.2 are merely indicated because they are hidden in this view by the spur gear 35 and by the spur gear 27.
  • a rotation of the shaft 36 causes a rotation of the driver 37, which in turn via the crank drive an axial stroke of the distribution cylinder 12.1; 12.2 causes.
  • the output to the traversing drive 22 can also take place at another point of the rotary drive train between the drive motor 18 and the distribution cylinder 12.2 or even on the other side of the machine located on the other end face of the Reibzylinders 12.2 pin 29 to a corresponding traversing gear 22. Also, if necessary, one of a worm drive 33, 34 different gear for decoupling the axial drive may be provided.
  • the traversing drive 22 and the traversing gears 22 are overall designed as a unit with its own housing 41, which can be designed additionally encapsulated.
  • the traversing gear 22 may be lubricated in the enclosed space either with oil, but preferably with a grease.
  • the traversing gear 22 is supported in the illustrated embodiment by a holder 42 connected to the side frame 31.
  • the drive motor 18 is in this case releasably connected to the housing 41 of the traversing gear 22.
  • Fig. 5 16 and 16 show an advantageous embodiment of a torsionally rigid connection between the axle portion 28 and the respective pin 29. This is with respect to a rotation about a frictional engagement, which by clamping a tapered portion of the pin 29 made by this comprehensive, slotted shaft portion 28 becomes.
  • the position of a clamping screw 43 is dimensioned such that it - at least partially immersed in a circumferential groove of the pin 29 - viewed transversely to the axis of rotation of the pin 29. It thus represents an interlocking securing of the connection with respect to an axial direction.
  • the prefabricated preferably as a module transmission unit can be completely pre-assembled as a subunit for example designed as a module inking 08 and be pre-assembled in an advantageous embodiment before use in the printing unit 01 on the side frame 31 of the inking unit module.
  • the modularity also allows the installation / replacement / replacement of the module designed as a transmission when the inking unit module is already inserted into the machine.
  • the dampening remoteness cylinder 12.1 does not have a rotational forced drive in the production direction of rotation, the rollers 11 (13) roll off each other largely without slippage, at least in the inking unit area remote from the dampening unit.
  • the drive motor 18, which drives the second distribution cylinder 12.2 both rotationally in the direction of production rotation and counter to the direction of production rotation can be designed as an electric motor which can be controlled with respect to its power and / or torque and / or also with respect to its speed. In the latter case, if the drive motor 18 is also operated in speed-controlled / pressure-controlled manner, then it can still be in the vicinity of the inking unit 08 in the vicinity of the dampening system. Problems arise with regard to different effective roll circumferences.
  • the drive motor 18 is advantageously designed such that it at least during the printing operation with respect. Its power and / or its torque is controlled or regulated. This can basically be done by means of a drive motor 18 designed as a synchronous motor 18 or as an asynchronous motor 18:
  • the drive motor 18 designed as an asynchronous motor 18, which in an associated drive control 46 ( Fig. 12 ) only one frequency, z. B. in pressure-down of the inking unit 08, as in Fig. 13 illustrated, and / or an electrical drive power or a torque in pressure on the inking unit 08, as in Fig. 12 represented, is given.
  • print-Ab of the inking unit 08 ie the applicator rollers 11 are out of rolling contact with the forme cylinder 07 ( Fig. 6 .
  • the inking unit 08 via the second distribution cylinder 12.2 can be brought to a suitable for the pressure-On-sites peripheral speed in production direction of rotation, in which the peripheral speeds of forme cylinder 07 and applicator rollers 11 only by less than 10%, in particular less than 5%, differ from each other.
  • This limit is also advantageous as a condition for the pressure-on-sites of the embodiments mentioned below.
  • a suitable frequency or performance or torque specification is empirically and / or computationally determined beforehand and held either in the drive control itself, a machine control or a control center computer, wherein the default value is preferably changeable by the operator. This also applies advantageously to the default values mentioned below.
  • the applicator rollers 11 are in rolling contact with the forme cylinder 07 and all rollers 11; 12.1; 12.2; 13; 14 of the inking 08 hired against each other, as shown schematically in the Fig. 1 . 2 . 4, 5 . 9 . 10 and 12 shown, the rollers 11; 12.1; 13; 12.2; 13; 14 to a part of the forme cylinder 07 via the now produced friction gear between the rollers 11; 12.1; 13; 12.2; 13; 14 in the production direction of rotation ( Fig. 2 . 4 and 9 ) or contrary to production direction of rotation ( Fig.
  • the drive motor 18 can be operated with a small (drive) torque or a small drive power, which only contributes to the rear of the inking unit 08 on the substantially predetermined by the frictional contact To maintain peripheral speed.
  • This drive power can be left constant in a first variant for all production speeds or speeds of the forme cylinder 07 and either correspond to those specifications for starting in pressure-Ab or represent their own constant value for production.
  • the frequency and / or drive power can be predetermined and stored for different production speeds and additionally, if necessary, for starting in pressure-off different specifications. Depending on the production speed, depending on the production speed, then the default for the drive motor 18 can vary.
  • the drive has in addition to the drive control 46 ( Fig. 12 ) and the asynchronous motor 18 of the first embodiment, a speed feedback, so that the drive motor 18 in the phase of the inking unit operation in pressure-Ab ( Fig. 6 . 11 and 13 ) With the speed of the associated forme cylinder 07 and the printing cylinder 06; 07 is essentially synchronized.
  • the actual speed detecting sensor 47 z.
  • a rotary encoder 47 on a rotatably connected to the distribution cylinder 12.2 rotating component, eg. Example, a rotor of the drive motor 18, the shaft 24, the shaft portion 28 or the pin 29, be arranged ( Fig. 12 ).
  • a rotary encoder 47 on a rotatably connected to the distribution cylinder 12.2 rotating component, eg. Example, a rotor of the drive motor 18, the shaft 24, the shaft portion 28 or the pin 29, be arranged ( Fig. 12 ).
  • a rotary encoder 47 having a co-rotating initiator and stationary sensor 47 is shown by way of example on the coupling 23, the signal of which is fed to the drive control 46 via a signal connection shown by dashed lines for further processing. Due to the speed feedback, the comparison with a rotational speed M representing the engine speed and a corresponding adjustment of the power or frequency specification, a slip at the moment of pressure on-position can be avoided or at least minimized to a few percent. In the print-on operation, the drive motor 18 is then preferably no longer strictly with respect to. The described speed feedback but essentially operated according to the above-described frequency or power specification.
  • a third embodiment has a synchronous motor 18 instead of the asynchronous motor 18 of the second embodiment.
  • a speed feedback and a related synchronization and control in the pressure-off phase is carried out according to the second embodiment, for. B. again in the drive control 46th
  • a drive motor 18, in particular a synchronous motor 18, is provided, which is optionally speed-controlled in a first mode (for inking unit 08 in print-Ab) and in a second mode with respect to a torque (for inking unit 08 in print-on). is controllable.
  • Drive control 46 and drive motor 18 preferably have an internal control loop for speed control, which, similarly to the second embodiment, comprises a return from an external rotary encoder 47 or an internal motor sensor system.
  • synchronous motors 18 are used, a plurality of these synchronous motors 18 of a printing unit 01 can be assigned a common frequency converter or converter.
  • a respect to versatility advantageous, but more complex development of the fourth embodiment is the formation of the drive motor 18 as an optional position and torque controllable servo motor 18, d.
  • H. a three-phase synchronous motor with a device which allows to determine the current rotational position or the angle of rotation with respect to an initial position of the rotor.
  • the feedback of the rotational position can via a rotary encoder, z.
  • each drive motor 18 is assigned its own frequency converter or converter.
  • the drive control 46 is advantageously in signal connection with a so-called virtual master shaft in which an electronically generated master axis position ⁇ circulates.
  • the circumferential Leitachsposition ⁇ serves the Synchronization, with respect to correct angular position and its temporal change (angular velocity ⁇ ) mechanically independent drive motors of aggregates, which are assigned to the same path, in particular drive motors of individual printing cylinders or groups of printing groups and / or the drive of a folder.
  • a signal connection to the virtual master axis can thus provide the drive controller 46 with the information about the engine speed.
  • the drive of the friction cylinder 12.2 is thus preferably moved by the drive motor 18 in such a way that the drive motor 18 is driven or regulated in a controlled manner in the case of the inking unit 08 running in the production direction of rotation but in the down position (ie parked applicator rollers 11) and when the printing press is running, as soon as a printing on the inking unit 08 (ie the applicator rollers 11) is done, the speed control or control is deliberately abandoned.
  • D. h. It is no longer held at a speed, but the drive motor 18 is in the further course of a torque, for. B. over a predetermined electrical power, and / or in terms of a controller on the drive motor 18, in particular asynchronous motor 18, adjustable torque operated.
  • the torque to be set or the power to be adjusted is chosen, for example, smaller than a limit torque, which would lead to a first rotation (under slip) of the driven in the production direction of rotation friction cylinder 12.2 at salaried, but with respect.
  • the load characteristic of a drive motor 18 embodied as an asynchronous motor 18 counteracts the behavior intended for the purpose here in such a way that, as the load increases, the frequency is reduced while the drive torque increases. Goes in the friction gear between form cylinder 07 and second Friction cylinder 12.2, for example, already much of the forme cylinder 07 derived drive energy and thus lost peripheral speed, so that the load of the drive motor 18 increases, so the increased torque is provided at a reduced frequency. Conversely, little torque is transmitted by the drive motor 18 - it runs virtually empty - if, for example, sufficient energy is transmitted via the friction gear to the distribution cylinder 12.2 in the production direction of rotation.
  • the inking unit 08 as in the Fig. 2, 3rd and 7 shown schematically, a constant distance of the distribution cylinder 12.1; 12.2 for all formats, so for different sizes and different web widths on.
  • Advantages of this result from the fact that regardless of the diameter of the forme cylinder 07 in the Fig. 4 b), 5 b), 6 b ) 8, 9 . 10 and 11 shown, identical or identical Querverreibgetriebe assembly 45 consisting of traversing gears 19, spur gear 20, 21 gear and traversing 22 for all formats, so for different sizes and different material web widths can be used.
  • At least one distribution cylinder 12.1; 12.2 is, for example, for maintenance or for inking from a in the Fig. 4, 5 . 9 and 10 shown, employed on an applicator roll 11 position in a in the Fig. 6 and 11 represented pivoted from the applicator roller 11 position preferably swung down at a standstill.
  • pivotable connecting rod mechanism 48 is provided to the at least one distribution cylinder 12.1; 12.2 to reduce ( Fig. 12 and 13 ).
  • the gear 35 and spur gear 35 is substantially as in Fig. 18 represented by a spur gear 53, which is connected by means of the freewheel 50 with the clamping hub 51.
  • the clamping hub 51 has a clamping screw 43 for clamping on the pin 29 of the distribution cylinder 12.1 ( FIGS. 15 and 16 ).
  • a draw bolt 55 is by means of a bearing 40, z. B. Rolling bearing 40 mounted in a bush 54 in the interior of the spur gear 53.
  • the bushing 54 ensures an axial alignment between the journal 29 of the friction cylinder 12. 1 or the clamping hub 51 and the tension bolt 55.
  • a groove nut 56 holds the roller bearing 40 on the tension bolt 55.
  • a bearing 52, z. B. bearings 52 and the freewheel 50 support the sleeve 54 radially from the spur gear 53 from.
  • the drive motor 18 of the or the distribution cylinder 12.1; 12.2 is not in positive drive connection with the forme cylinder 07th
  • At least the form cylinder 07 to be inked by the inking unit 08 has a different, preferably angle-position-controlled drive motor than the inking unit 08 driven by the drive motor 18.
  • each of the forme cylinder 07 and each of the transfer cylinder 06 has its own angular position-controlled drive motor.

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  • Inking, Control Or Cleaning Of Printing Machines (AREA)

Claims (10)

  1. Groupe d'encrage (08) d'une machine à imprimer pour l'encrage d'un cylindre porte-cliché (07), lequel comporte un train de rouleaux avec au moins un premier rouleau de transfert (12.1), le ou les rouleaux de transfert (12.1) étant entraîné en rotation par un moteur d'entraînement (18), caractérisé en ce qu'une une roue libre (50) est disposée entre le premier rouleau de transfert (12.1) et le moteur d'entraînement (18), en ce que le premier rouleau de transfert (12.1) n'est entraîné dans un sens de rotation de production que par friction avec des rouleaux (11 ; 13) adjacents, en ce que le premier rouleau de transfert (12.1) est entraîné en rotation par le moteur d'entraînement (18) contre le sens de rotation de production, et en ce que ledit groupe d'encrage (08) comporte au moins un deuxième rouleau de transfert (12.2), entraîné en outre par un moteur d'entraînement (18) en rotation forcée aussi bien dans le sens de rotation de production que contre celui-ci.
  2. Groupe d'encrage selon la revendication 1, caractérisé en ce que le premier rouleau de transfert (12.1) et le deuxième rouleau de transfert (12.2) sont entraînés par un moteur d'entraînement (18) commun contre le sens de production.
  3. Groupe d'encrage selon la revendication 1, caractérisé en ce que le moteur d'entraînement (18) et une commande d'entraînement (46) associée sont réalisés de telle manière que la puissance et/ou le couple du moteur d'entraînement (18) sont commandés ou régulés au moins pendant un mode d'impression en position d'application de pression du groupe d'encrage (08).
  4. Groupe d'encrage selon la revendication 1, caractérisé en ce que le premier rouleau de transfert (12.1) n'est entraîné dans le sens de rotation de production que par friction, et le deuxième rouleau de transfert (12.2) est entraîné en outre par le moteur d'entraînement (18) en rotation forcée dans le sens de rotation de production.
  5. Groupe d'encrage selon la revendication 1, caractérisé en ce que les rouleaux de transfert (12.1 ; 12.2) sont entraînés en va-et-vient forcé par un engrenage oscillant (22) commun.
  6. Groupe d'encrage selon la revendication 5, caractérisé en ce que l'engrenage oscillant (22) est entraîné par le moteur d'entraînement (18).
  7. Groupe d'encrage selon la revendication 1, caractérisé en ce qu'un premier rouleau de transfert (12.1) entraîné exclusivement par friction dans le sens de rotation de production n'est entraîné en va-et-vient forcé que par un engrenage convertissant en mouvement axial la rotation dudit rouleau de transfert (12.1), et sans liaison de transmission mécanique avec un entraînement oscillant (22) d'un autre rouleau de transfert (12.2).
  8. Groupe d'encrage selon la revendication 1, caractérisé en ce que le rouleau de transfert (12.1) entraîné exclusivement par friction dans le sens de rotation de production, et pourvu d'une liaison de transmission mécanique avec un moteur d'entraînement (18), transmettant un couple pour l'entraînement contre le sens de rotation de production, est relié au moteur d'entraînement (18) par un engrenage (35) disposant d'une roue libre dans le sens de rotation de production, et d'un embrayage à transmission de couple contre le sens de rotation de production.
  9. Groupe d'encrage selon la revendication 1, caractérisé en ce que le moteur d'entraînement (18) du premier rouleau de transfert (12.1) et/ou du deuxième rouleau de transfert (12.2) ne comporte aucune liaison de transmission à crabotage avec le cylindre porte-cliché (07).
  10. Groupe d'encrage selon la revendication 1, caractérisé en ce que le cylindre porte-cliché (07) à encrer par le groupe d'encrage (08) est entraîné par un moteur d'entraînement différent du moteur d'entraînement (18) du premier rouleau de transfert (12.1) et/ou du deuxième rouleau de transfert (12.2).
EP08786488.0A 2008-02-08 2008-07-28 Dispositif d'encrage d'une presse à imprimer Not-in-force EP2195166B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102008000257A DE102008000257B4 (de) 2008-02-08 2008-02-08 Farbwerk einer Druckmaschine
PCT/EP2008/059842 WO2009097912A1 (fr) 2008-02-08 2008-07-28 Dispositif d'encrage d'une presse à imprimer

Publications (2)

Publication Number Publication Date
EP2195166A1 EP2195166A1 (fr) 2010-06-16
EP2195166B1 true EP2195166B1 (fr) 2014-05-07

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US (1) US8322281B2 (fr)
EP (1) EP2195166B1 (fr)
CN (1) CN101925461B (fr)
DE (1) DE102008000257B4 (fr)
WO (1) WO2009097912A1 (fr)

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DE102011076336A1 (de) 2011-05-24 2012-11-29 Koenig & Bauer Aktiengesellschaft Vorrichtung zur Temperierung, Druckturm für den wasserlosen Zeitungsdruck sowie Zeitungsdruckmaschinen
DE102011078283B4 (de) * 2011-06-29 2015-01-22 Koenig & Bauer Aktiengesellschaft Rotationsdruckmaschine mit einem Formzylinder und einem an diesen Formzylinder angestellten Farbwerk
DE102011082001B4 (de) 2011-09-01 2014-05-15 Koenig & Bauer Aktiengesellschaft Vorrichtung zur Temperierung rotierbarer Bauteile von Druckwerken einer Druckmaschine, Druckmaschine sowie Verfahren zur Temperierung einer Druckmaschine
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DE102013015470A1 (de) * 2012-10-04 2014-04-10 Heidelberger Druckmaschinen Ag Druckmaschine mit einer Schalteinrichtung für eine changierende Walze
CN103963452B (zh) * 2014-05-08 2016-06-22 周玉翔 一种墨辊张力调节机构
DE102016205348A1 (de) 2016-03-31 2017-10-05 Koenig & Bauer Ag Antriebsanordnung für eine Bogenverarbeitungsmaschine
DE102016205342B4 (de) 2016-03-31 2019-06-13 Koenig & Bauer Ag Verfahren zur Regelung eines Drehmomentes eines Formzylinderantriebs
CN107854870A (zh) * 2017-12-11 2018-03-30 北京北排装备产业有限公司 一种非金属链条式刮泥机链条张紧装置及其使用方法
DE102018118100A1 (de) * 2018-07-26 2020-01-30 Ebm-Papst St. Georgen Gmbh & Co. Kg Pumpe mit absoluter Drehwinkel-Erfassung

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Also Published As

Publication number Publication date
US20100319560A1 (en) 2010-12-23
US8322281B2 (en) 2012-12-04
DE102008000257A1 (de) 2009-08-20
CN101925461A (zh) 2010-12-22
DE102008000257B4 (de) 2010-05-12
EP2195166A1 (fr) 2010-06-16
WO2009097912A1 (fr) 2009-08-13
CN101925461B (zh) 2012-11-28

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